System for controlling the position of a shaft in its bearings



ET GT Dec. 29, 1953 P. GERARD AL 2,663,977

' SYSTm FOR GONTROLLIN HE POSITION OF A SHAFT IN ITS BEARINGS Filed July's, 1950 s Sheets-Shah 1 Inventors I v Dec. 29, 1953 P. GERARD ETAL 2,663,977

SYSTEM FOR CONTROLLING THE POSITION OF A SHAFT IN ITS BEARINGS Filed July 8, 1950 8 Sheets-Sheet 2 NG THE POSITION TS BEARINGS Dec. 29, 1953 E RARD SYSTEM CONTROLLI OF SH FT IN I a Shee ts-Sheet 5 Filed July 8, 1950 wag F. GERARD ET AL Dec. 29, 1953 2,663,977

SYSTEM FOR CONTROLLING THE POSITION OF A SHAFT IN ITS BEARINGS 8 Sheets-Sheet 4 Filed July 8, 1950 Dec. 29, 1953 P. GERARD ETAL 2,653,977

SYSTEM FOR CONTROLLING THE POSITION OF A SHAFT IN ITS BEARINGS Filed July 8, 1950 8 Sheets-Sheet 5 AH-o q:

Dec. 29, 1953 p GERARD ET AL 2,663,977

SYSTEM FOR CONTROLLING THE POSITION OF A SHAFT IN ITS BEARINGS Filed July 8, 1950 8 Sheets-Sheet 6 Invent rs I I Mr W Aim-hey:

Dec. 29, 1953 P. GERARD ET AL SYSTEM FOR CONTROLLING OF A SHAFT IN ITS THE POSITION BEARINGS 8 Sheets-Sheet '7 Filed July 8, 1950 NET Dec. 29, 1953 1 P. GERARD ET AL 2,663,977 SYSTEM FOR CONTROLLING THE POSITION OF A SHAFT IN ITS BEARINGS Filed July 8, 1950 8 Sheets-Sheet 8 this example, bearing 2 is a f Fig. 2) comprises in shifting said mon axis of bearings 2 and 3. Assuming that chambers 5 and 6' have a vertical axis while be seen that axis Y-Y be displaced with respect to the common axis of V bearings 2 and 3 to come into position Y1-Y1.

the feeding section of zone 8- is increased while that 3 pressure control means in diametrically opposed zones, by means of one single distributor, the movable part of which constitutes a naember scanning on a templet.

Fig. 8A shows a shaft journalled in two fluid bearings periodically controlled by means of a distributor rotatively driven'from said shaft.

Fig. 9 shows a machine for grinding revolution bodies, having incurved generatrices in which the grinding-wheelshaft is journalled in two bearings, one of which is provided with control means comprising a distributor, a scanning member and a templet integral with the work-carriage.

Fig. 10 is a section showing in detail the bearings of the grinding-wheel shaft of Fig. 9. v

Fig. 11 is a partial view of an alternative embodiment of the machine shown in Fig. 9, comprising an auxiliary scanning member for the diamond-shaping of the grinding-wheel.

Fig. 11A is an axial section of the diamondshaping scanning member of Fig. 11.

Fig. 12 is an elevational partial view of a machine for grinding non-revolution surfaces provided with means to control the position of the part-driving spindle according to the invention.

Fig. 13 is a plan part view of a machine also adapted to grind non-revolution surfaces and provided with the system according to the invention.

Fig. 14 shows a bore-grinding spindle journailed in bearings, one of which is provided with control means according to the invention.

Fig. 15 is an end view of the spindle of Fig; 14. v V

Figs. 16 and 17 show the part-driving spindle of a jig-borer, said spindle being journalled in ously decreased, axis YY of shaft I will come into position Y2Y2 (see Fig. 1).

By using the control means shown in Fig. 2, the shaft being journalled in bearings of the type of Fig. 1, said shaft will be easily brought into any desired angular position with respect to the common axis of the hearings in that horizontal plane which contains said common axis,

two bearings, one ofwhich is controlled according to the invention. 7

It will be noted that, in most instances, the clearance between the fixed and movable elements of the bearing has been considerably exaggerated in the drawings, for clarity of illustration.

Referring first to shaft journalled in two Fig. 1, there is shown at l a bearings '2 and 3. In

knee-joint mechanical bearing in which the shaft axis is free to move angularly about point 4 located on the bearing axis.

Bearing 3 is afiuid bearing. According to a first embodiment, bearing 3 (see two feeding zone 5 and 6 fed from a suitable pressure fluid source (not shown) through a duct 1 and two chambers 8 and 9 fed by the same duct 1 but through two devices It and H capable of varying the feeding sections.

There is shownat l2 longitudinal outlet grooves for the pressure fluid.

It will be understood that when the feeding 1 sections of ducts l3 and. I4 which feed chambers 8 and 9, respectively, are varied, e. g. by increasing the feeding cross-section of duct H, while I l decreasing that of duct under the control of devices l0;

l3, the shaft is imparted and H with a leftwards displacement (in Fig. 2) which results shaft with respect to the comchambers 8 and 9 have a horizontal axis, it will of shaft I (see Fig. 1) will When, conversely,

of zone 9 issimultanebodiment of the and M of Fig. 2. As

position in which it will be maintained during any desired time, said shaft then rotating about its off-set axis without risking that the stresses exerted upon the shaft vary in any noticeable manner the position of its axis with respect to the common axis of the bearings.

In Figs. 3 and 4 is shown an embodiment of a distributor according to the invention permitting controlling the feeding sections of ducts l3 described above, it is suitable to control said sections so as to meet the three desired conditions, namely that the variations are proportioned to the displacements of the control member, that they are in opposite directions and simultaneous, and that they are such that the sum of the feeding cross-section remains constant. The distributor shown in Figs. 3 and 4 is capable of perfectly meeting said three conditions. This distributor is constituted by a body I5 in which is provided a bore l6 fed through a duct 1 with a pressure fluid supplied by a suitable source (not shown), the two ducts l3 and [4 leading from diametrically opposed points of said bore. Said distributor thus assumes in fact the functions of both cocks l0 and H (see Fig. 2). In bore [6 is mounted a slide valve l8 having a profiled portion 19. The pressure fluid is brought through a passage 23 into the peripheral zone of the profiled portion 18. Said slide valve comprises an extension constituted by a rod 21 which either constitutes itself the scanning member ac- 40 cording to the invention or alternatively a part solid with such a scanning member.

A longitudinal groove 22 is provided on the periphery of rod 21 and a lug 23' integral with a knurled ring 24 is engaged in said groove so that when said knurled ring is rotated, this motion results in a rotation of rod 2! around its own axis. Lug 23 is however capable of sliding freely in groove 22 which permits a longitudinal displacement of rod 2! in either direction within the limits of the length of said groove 22.

The axial displacements of the scanning member 2| due to the scanning of a suitable templet cause, thanks to the shape of the profiled portion I9, equal and opposite variations of the feeding cross-sections of ducts l3 and it.

Moreover, the rotation of the knurled ring.

lar'position so that the above-mentioned section variations may be given any desired value for a well-defined displacement of rod 21.

In particular, if the'proiiled portion [9 is set into a position perpendicular to that of Fig. 3, both feeding sections of ducts i3 and M are made equal to each other, whichever may be the axial position of slide valve it, so that the controlled shaft then assumes a fixed position. y

In Fig. SA, has been shown a constructive emslide valve of Fig. 3 completed by a graduated scale for measuring the displacements of the knuled ring 24 which permits adjusting with accuracy the sensitivity of the apparatus and by another graduated scale along rod 2| to indicate at any instant the axial position of the scanning member. The distributorof Fig. 3A further comprises safety nozzles a, mounted "ag'feeeeev r so es to "connect-the iriletduct-"Pdireetiywith the outlet ducts +3 and "F4 leading to the pressure zones 8 and 9, "respectively, =-'so that these zones will be always -'supplied-through the='by=pass==noz- -zlesa with a'small amount-of pressure fiuidindependently of the position of slide valve 1 8 -to thereby prevent meta-l to-metal eontaet between shaft I and-a portion o f the bearing suiface when one of the ducts l 3 and 4 4 s'hould be -completely closed by theslide v-alve t8, thatis to say when the supply of pressure-fluid through th'e distributor to one of thepressurezones t and 9 -is interruptedin response to 'a corresponding :ipositioni o'f the slide valve.

According to anotheremb'odimentshown in #Fig. "5, -th'e fluid bearing 3 -(Fig. 1) comprises five periodically controlled feeding zones 25%, "215B, 2-5'Cj-125D, 25E fed 'witha -pressure fluid through "suitable 'ducts -26 by a five way: distributor ewhich periodically controls-the; feeding cross-"sectionsiof thefivezones 25.

The distributor oran es is shown in axialiseotion in Fig. 6. In this figure. there: is ashowniat 1328 the distributor body which is :provided "with a cylindrical axial bore 29 in which is slidablyiand rotativly mounte'd a slide valve comprising a :profiled portion..'3 lcomprisedsibetween ltwoa'cylin- 'dricaliportionsl3'2iand 33. Said slide valve comprises an extension constitutedi'byr a'rodzsl screwed at 35in 'a'roller36 use'difor rotatively driving the :slide valve. Rod .34 :has; aadiameter smaller vthan the lower cylindrical portion 3'3 ofthe slide valve whichdetermines anannular shouldering's i upon which a threaded'ring 38;screwed;on the adistributor :body :28 is capable: of acting.

'The angular space betweensportion 31" and the :wall of bore-:29. communicates awiththefive ports A, B, C, 'D, E of. the distributor (Fig. connected through the above-mentioned ducts 25' withzfeedzin'gzonesz' of thebearing: indicated-by :thesame "reference. letters. It maybe-seen that-the angular positions .of the feedingzones 2-5A to=25E, re-

spectively, correspond to those, of ports --A-.to E -of the distributor.

ZIt-will be easily understood that therrotation I of slide valve 3| about its'axis-causes in the-be-aring a corresponding rrotation of the;shaf;t-axis around the bearing axis. Thethreaded-:ring '33 permits adjusting at will the axial vposition of -the:slide valve .3 I, which permits determining the \magnitude of the :eccenric:shift-ofthe. shaftlin the bearing. m

When the slide valve .is .axially.. displaced in bore29 of the distributor. by-means of ring 3'8 so that an annularvportion 39 of the profiled mem-.

ber-v3l comes tolieadjacent-the passages illlgiving access to the above-mentioned ports A, B, .QD, E,

a maximum eccentric shift is obtained inthe hearing the displacements of "the shaft occur lring in phase with those of the slide valve, as

.shown in Fig.5. However, when the annular por- -tion ll of the profiled membertil is brought adjacent the passages '40, the rotation of said slide valve will cause no displacement of shaft i in itsbearing, since the shaftiis then in itsconcentric position. Finally-,When the annularportionlZ is'located at'the level oL-passagesf fl), a maximum eccentric displacement of the 'shaft is obtained in a direction opposite tothat mwmen the shaft is displaced when the annular portion 39 is adjacent passages 40. If slide valve "3|,Linstead of 'beinggiven only the rotary motion indicated above,'is also axially displaced I in bore '29'by means of"ring"'38, it 'willbe poss'ibleto obtain corresponding complex displacementsac- -he constructive embodiment-of Fig. the jshaft =-ma-y' be s'hifte'd it two bear-i'ngs' h ih are -ofthe-typeofFig. 2, s axis may be dis placed in 'a plane aboiit a point'='locaited between the -two bearings ami on their common =a -x is. m *the embodiment o'fi' ig. 8A,- the" two' bear-in gsaa i-e -:cr=- the-periodic coritrl type hown in Fight-and *the shzi'f-t can be impar-ted with *a -precessional *motionaround the common-axiscam b'ea'rings, the axis of said shaft describinga cone;-the apex or which is located between the two *bea-r'ings. These two embodimentscomprise *oneeingle distributor controllin'g simu-ltaneously both bear ings under tlre-actionofa' member "seanninga'templet inthecaseof Fig. =8 "and under the control ef the shaft itself-in the case of Fig. ea. ites-abacus "thata separatedistributor-might*be provided ior -ea'ch'bearing and that;moreoveryone of the shaft bearing-s might b'e' of the type 'shown in Fig/58, "while the *other bearing wed-Id Ebeo'f the type Y -35 a control with a"relative'==ph'ase=shift loy ISO in thetwo-bearings}it-isobvi'ous that saidishaft axis might be caused t describeeither a cylindrieal surface by "a common-m phase ef both bearings or a hyperboloid '-surface *by- "a simultaneous but 40 phase-shifted control ofbothbear-ings.

In-the example shewn-in Fig.-'8A; shaft lcarries agrinding wheel Hw-and the reduction ratio of gears I04 is high so that the =preces'sionakmotion of the 'shaft" is slow with'"respect' to its rotational 5 "motion. I-n the constructive ='eni -bedimentshown in -Fig-s, shaft "1 "is iournalled intwofi-uidtearings 43 of the type shown diagrammaticallyafifl *(Fig 1-)' and indetaJili-rriig." Zfleach bearfin'g'c'omprising two diametrically opposed, pres- "sure-"control "feeding'fzones ":8 and B. *Said zones are connected in parallel tinoughtwo duets 13 and M with a distributorprovided-withaprdfild "slide "valve similar to that "previously described with reference" toFigs. Wand-"4.

It will bennderstoo'd"that'whemmember Zlfis scanningtemplet'fl ;it'moves'axially =a's"a-func- 'tion "of the curvature "of the "templet profile. Thanks to theshape" of'theprofiledslidevalve, 1 theeross=sections of" thepassagesjgivingaccessto 'dufcts l3 and i 4' vary 'in*the" S a,I ,1e extent "biitin opposite directions; 'sothat"e:"g:the feeding cross- "section of "zones 9 of both bearings increases, while thatof thefeeding zones rofbothbearin'gs is reduced inthe' sameextent. It willbeurider- :stood that'whenthe:slide'valveslidesintnliore of the distributor, the axis'of shaft l is"displaced about; point 0 Tlocate'd 'on'the common axis of'said jbearin'g and"substantially'mid=way between the I I "same.

In the embodiment "shown in Fig; 8A,''sha Tt I .is linked witharOtor 3| (Era-rotary"distributor through a'suitable' helical "gear train H14 having such arati'o that rotor'j3 l"rotates far'slowerthan shaft I. The "rotary distributor controlled by respectto the rotation of said rotor. Thus, the rotation axis of shaft i is imparted with a slow .precessional motion around the common axis of both bearings and said rotation axis describes a conical surface, the apex of which is located midway between bearings and 106. Gear I04 is also located mid-way between the bearings, the

spacing between the axes of the two pinions being thusbut slightly influenced by the precessional -motion of the shaft.

Fig. 9 shows a machine for grinding revolution bodies, the generatrices of which are incurved, .said machine being provided with the control system according to the invention. Said machine comprises a frame 50 carrying slides 51 on which is slidably mounted a table 52 carrying in turn a work-headstock 53 which supports in conjunction with a tailstock 54 the work P. Moreover, headstock 53 rotatively drives said work. The

grinding-wheel carriage 56 is mounted on a sec- :ond pair of slides 55 also carried by frame 55.

Said carriage supports in turn the grinding-wheel spindle l which is journalled in bearings 59 and 60 and other elements (not shown) imparting said spindle l with its rotary motion. The grinding-wheel proper is shown at 51.

;. Bearing 60 is of any suitable type. It may be ,eitherya mechanical bearing, e. g. of the kneejoint type or a fluid bearing such as described in the above-mentioned patent applications and as shown in the drawings. 7

-Bearing 59 is provided with a control system of the position of the grinding-wheel spindle i according to the invention.

In Fig. are shown in detail two controlled bearings similar to 59 and constituting an alternative mode of bearing of spindle 1 shown in Fig. 9.

A pump 6! and a regulating valve 62 discharge into ducts 63 and l a fluid under a substantially constant pressure. fhe fluid tank is shown at R. A duct 8d branched off duct 53 leads the constant pressure fluid to bearing 50.

Inthe example shown, bearing 59 is of the type shown diagrammatically at 3 (Fig. 1) and in detail in Fig. 2. Said bearing comprises four feeding zones, viz.; two feeding zones of vertical axis .fed from an annular chamber fed in turn through the constantsectionduct 63 and two zones of horizontal axis provided with a variable feeding and connected with ducts 66 and 6? which may be set into communication with two other ducts J3 and i4 by means of a rotary distributor l0. When the rotary member of distributor 10' is in U the position shown in Fig. 9, it may be seen that duct i4 communicates with duct 66, while duct l3 communicates with duct 61; Conversely, if said rotary member is brought into a position perpendioular tothat shown, duct is is set into communication with duct 81 while duct 13 is set into communication with duct 66. ihis arrangement permits reversing the directionof the transaxial shift imparted to the grinding-wheel spindle I.

. Thus, in one position of the rotary distributor III, the grinding-wheel is imparted with a dis-- placement corresponding to theoutline of templet 8 41 and incurvedin the same direction as said outline, while in the other position of said distributor, the grinding-wheel is imparted with a displacement corresponding to the above-mentioned outline but incurved in the opposite direction.

The cross-sections of ducts l3 and it may be varied at will and in opposite directions by means of a distributor l5 similar to that shown in Fig. 3. Said distributor is controlled by a scanning member 21 sweeping on templet 41.

It will be understood that thanks to the invention, it is possible to obtain revolution bodies having incurved generatrices with the greatest accuracy, due to the fact that the only element to be displaced is the spindle carrying the grinding-wheel and that the displacements of said spindle may be controlled with accuracy and sensitivity. The accuracy and sensitivity are further increased thanks to the sensitivity-adjustment facility of distributor i5. It is thus possible to use a templet having a noticeably incurved outline to obtain a desired piece outline corresponding to said templet outline but only slightly incurved.

In the alternative embodiment of the above described grinding-machine shown in Fig. 11, there is provided, apart from the parts heretofore mentioned, an auxiliary scanning member 2 la sweeping on an auxiliary templet 41a carried by the tailstock 58 which also carries a diamond 18. The device of Fig. 11 is also provided with a threeway cock M permitting feeding at will either through a duct '1 the normal distributor [5 controlled by the main scanning member 2! sweeping on the main templet 41, in order to grind revolution pieces as desired or through a duct 1a the auxiliary distributor I50. to suitably shape'the grinding-wheel. The auxiliary distributor [5a varies, under the control of scanning member 2 la in opposite directions and in the same extent, the cross-sections of ducts 13a and Ma. connected with ducts B6 and 6?, respectively. This arrangement permits also shaping the grindingwheel by means of diamond 18 so as to give the periphery of said grinding-wheel the desired outline which is determined by the templet outline 47a. The templet outline Ma. is so designed that the grinding-wheel, whatever may be the inclination of the spindle, never presents to the surface to be ground a leading cutting edge. The machine modified as shown in Fig. 11 thus permits, without any part removal, by a mere cock control, to shape the grinding wheel with the above-mentioned diamond at any desired time. Suitable means are provided to avoid any undesired communication in the scanning member, which is then at rest, between the two zones fed through the variable section of the scanning member when operative. In the embodiment shown in Figure 11A, said means are constituted by an abutment 51 maintained against rod 21a by the spring 98. .When rod Zia. is at rest, the groove 99 comes opposite the abutment 97 which is 'moved by spring 98 into the said groove, thus releasably locating the member Zia in the position in which its upper cylindrical part interrupts communication between the said two zones. The diamondshaping distributor may be constituted, as shown in Fig. 11A, in the same manner as the distributor of Fig. 3, but it is simplified in that it does not comprise any sensitivity-adjustment means; on the other hand, it is provided with a drawback spring 49.

nonerevolution surfaces in' which thaposition: of

-the-grinding-wheel spindle is controlled. by the system. according" to the invention; There is shown at 84 a rotary templet the outlineof which, e; g. oval, is used to determine the section. to. be given to the work. A- scan-ning member 2 i sweeps on said outline whichacts as a cama-nd'controls a distributor l5'of thetype describedabove (Fig. 3 which variesin opposite directionsand in-the same extent the cross-sections of ducts. is and l 4-. Thefeeding of distributor l5-is ensured by a duct '1. The work'P, mounted on a mandrelBZ is carried. by a work-holding headstock 53.3 and is rotativelyfast with. the; abovermentioned: templet. or cam 84. Thescanningmember' 21' is SOIid'iV/Tith table 52. Itwill be understood thatwhenamam drel .82, workP and cam .84. are rotating; thezdise placements imparted to the scanning: member it cause corresponding displacements of" the 'grinding -wheel' shaft: in. its? hearing; so that" the part? obtained has a cross-section corresponding to that of cam 84.

:In the alternative embodiment shown" in Fig. 13;- the" machine still comprises arotary templ'et 8'4 but; in .this modifi'cation, it is the" front bears i'ng 59 f the work-holding headstock which" is controlled-by the distributor. Since the'con'trolled bearing which causesthe generationof the desired outline is that of the work-holdingheadstock, the grinding-wheel may be substituted by a suit'alile lathe tool' such as 92. Thearrangement of tlie machineof Fig; 13"is otherwise similar to that of Fig.- 12. Itwill be alsopossible to provide two similanc0ntrol1ed bearin'gs for the work holding headstock of'Fig; 13, said bearings being fed? by" one A single scanning member: It will be evident that the displacements of the shaft, referred to above; can actually amount to a: few thousandths ofan inch maximum, but shaping even on such aminute scale isfrequently im portantand the apparatus shown hereinpermits effectin'gthe desired result with extreme accuracy. As previously noted,,the displacementsareshown in-tlfe drawings onan exaggerated scale iniorder to make them" readily visible;

(1 Figs; 14- and 15 show-"another" embodiment of the invention; used with a spindle for'ifinishing hores. In these figures, there is'shown: at? I a spindle'carrying' atone: end a; suitable tool such as a grindi ng wheel 51a adapted togrinda bore such as*95. At its end'opposite to grinding-wheel Ta;.spindle lis' journalled' in a bearingofany suitabl'extypeiwhich may be e; g. a knee-joint ball bearing 96; butwhich might be also a fluid. bearing suchas describedin. the above-mentioned patent applications. Towards its end carrying grindingewheel 'd'la, spindle l is journa'll'ed ina bearing 91 provided with periodically controlled feeding zones. When the feeding cross-sections of'the different zones of bearing 91 arejvaried periodically, as described above; axis Y'-Yfof"said' shaft describes a conical surface around the common axis of bearings 96. and 91- and. grinding: wheels'la which rotates besides aroundsaid axis Y Y successively attacks all pointsof thepee riphery, of bore 95 and grinds'the same with accuracy. The driving; pulley of the spindle is shown at 98..

Theamp-litudeofthe precessional motion of spindle I. is progressively increased. and the bore thusmacliined assumes .a diameter. which is. not that ofthegrinderbut that of the envelope sur face-ofv the variousrpositions .of the: grinder. in

I precessionalmotion of thespindleaxis so as to sweeten:

1 3 spacer It..suffices.- to. acts upon-therotary dis-. tributor: (seeFig; 6 toreverse thadirectionof machine. the bore.-.in: the opposite direction- Eigs. 16: and. 17 show another embodiment adaptedtoa jigs-borer inwhich the upper bearing; I 00.- of spindle- I is. of. anorznal r'luidtype,

while the lower bearing 99 is providedwithcon? trolled feeding zones. according tolthe invention,

capable ofimpartingspindle. [witha precessional withahigh-accuracy. This devicepermits ad:

iust-ingi the.:diameterl; of the bore. obtained: duringe.theeworkingyotthe' machine. For example, thejigeborer. spindleshownin Figs. 16 and 1.7 may bedesigned: according tothe constructive embodiment of 8A, except thatthegrindingwheel would therrbe substituted-byasuitable jigborer tool.an'd.-. thatthe-ratio of the gear; train interposed betweenthe spindle: and: the: rotor of the rotary distributor would then; correspond to. a. transmissionv ratio equal to unity; so. that thespindle describes one-precessional cycle for each rotational turn-.1

Whatis claimedisz.

1. In combination,. a. rotatable shaft; at. least two. bearing structures. to'journal saidishaft, one a-ti-least. of sa-idbearing structures being, of the typein which .-the shaft-.isifloatably supportedin the stationary bearing surface, the, samecome prising a; plurality of circumferentially spaced pressure zones separated: by outlet. grooves and at least two. of" which zones arediametrically opposed, ,mea-ns'to feed separately pressure fluid to each of said zones-and controlmeans adapted to act-differentially: uponlthe feeding/of two di-v ametrically opposedzones-ofatleast one of'said bearingstructures; so as: to. shiftat will said shaft in respect tosthevlongitudinal common axise of said bearing structures by -a. displacement: in:a plane containing. said common 1 axis and the; di-

ametral. direction passing through :the centers of said: two feeding; zones.

2.1m. combinatiomai rotatable shaft, at least tworbearingstructures; to: journal said. shaft, one at; least. of. said bearing structures being ofthe type-in which .the shaft isfloatably supported in theestationarybearing surface; the same comprising. a; plurality, of circumferentially spaced pressure-"zones separated by outlet grooves, means to: feed :separatelyxpressure. fluid to. each of said zones and 1 means: to control. at .will the feeding of at" least :three; of. said: zones. of at: least one. of said,ebearingzstructures, so as: to shift at will said shaftinrespectzto thexlongitudinal common axis of said bearinggstructures; by. a displacement in the-plane containing said axis and thesresultant of the pressures in said controlled. zones.

3 In. combination a rotatable-shaft, at least two bearing, structures. tojournal saidxshaft, one at least: of said: bearing, structures being of the. type .inwhich the. shaft 'is. floatably supported in the: stationary bearing; surface; the same com prising.- a:: plurality,- of. circumferentially spaced pressure-zonesseparated lay-outlet grooves, means to feed separately pressure fluid to each of said zones and means to control periodically the feeding of at least three of said zones, so as to shift at will said shaft in respect to the longitudinal common axis of said bearing structures, so as to obtain complex movements of said shaft and, in particular, a precessional motion around said common axis.

4. In combination with a fluid bearing for a shaft rotatable in a stationary support, comprising a plurality of circumferentially spaced pressure zones in the stationary bearing surface, separated by outlet grooves at least two of which zones are diametrically opposed, and means including feeding ducts to feed separately pressure fluid to each of said zones, a distributor adapted to differentially control the feeding of two diametrically opposed pressure zones, by varying simultaneously and in opposite directions the cross-sections of corresponding feeding ducts in such a manner that said variations are a function of the displacements of its movable control member, and means to adjust the ratio between the displacements of said movable control member and the variations of said cross-sections.

5. In combination with a fluid bearing for a shaft rotatable in a stationary support comprising a plurality of circumferentially spaced pressure zones in the stationary bearing surface, separated by outlet grooves at least two of which zones are diametrically opposed, and means including feeding ducts to feed separately pressure fluid to each of said zones, a distributor adapted to differentially control the feeding of two diametrically opposed pressure zones, by varying the cross-sections of corresponding feeding ducts proportionally to the displacements of its movable control member, in opposite directions, simultaneously and so that the sum of said crosssections remains always constant, said distributor comprising a body, a cylindrical bore in said body, two diametrically opposed passages leading from said bore, each towards a duct feeding one of said pressure zones, a pressure fluid inlet to said bore and a movable valve member mounted in said bore and slidably displaceable by a scanning member, said movable valve member having a shape so designed that its axial displacement in either direction increases the cross-section of one of said duets while decreasing to the same extent the cross-section of the other.

6. In combination with a fluid bearing for a shaft rotatable in a stationary support, comprising a plurality of circumferentially spaced pressure zones in the stationary bearing surface, separated by outlet grooves at least two of which zones are diametrically opposed, and means including feeding ducts to feed separately pressure fluid to each of said zones, a distributor adapted to differentially control the feeding of two dia-' metrically opposed pressure zones, by varying the cross-sections of corresponding feeding ducts proportionally to the displacements of its movable control member, in opposite directions, simultaneously and so that the sum of said crosssections remains always constant, and means to adjust the ratio between the displacements of said movable control member and the variations of said sections, said distributor comprising a body, a cylindrical bore in said body, two diametrically opposed passages leading from said bore, each towards a duct feeding one of said pressure zones, a pressure fluid inlet to said bore and a movable valve member mounted in said bore to be slidably displaceable by a scanning member and angularly displaceable for adjusting at will said ratio, said movable valve member having a shape so designed that its axial displacement in one or the other direction increases the cross-section of one or the other of said ducts while decreasing, to the same extent, the cross-section of the other, whilst the angular displacement of said movable valve member produces simultaneously and in opposite directions a variation of said cross-sections, the sum of said cross-sections always remaining constant.

'7. In combination with a fluid bearing for a shaft rotatable in a stationary support, comprisin a plurality of circumferentially spaced pressure zones in the stationary bearing surface separated by outlet grooves and means to feed separately pressure fluid to each of said zones, a distributor to control periodically the feeding of at least three of said zones by varying periodically the cross-sections of feeding ducts of said zones, said distributor comprising a body provided with a bore, a movable valve member rotatably mounted in said bore, a pressure fluid inlet in said bore, radial passages leading from said bore towards each of said feeding ducts, the angular position of said radial passages corresponding to the angular position of said pressure zones and means to rotate said movable valve member. whereby the cross-sections of said ducts are periodically varied.

8. In combination with a fluid bearing for a shaft rotatable in a stationary support, comprising a plurality of circumferentially spaced pressure zones in the stationary bearing surface separated by outlet grooves and means to feed separately pressure fluid to each of said zones, a distributor to control periodically the feeding of at least three of said zones by varying periodically the cross-sections of feeding ducts of said zones, said distributor comprising a body provided with a bore, a movable valve member slidably and rotatably mounted in said bore, a pressure fluid inlet in said bore, radial passages leading from said bore towards each of said feeding ducts, the angular position of said radial passages in the distributor corresponding to the angular position of said pressure zones in said bearing surfaces and means to rotate said movable valve member, whereby the cross-sections of said ducts are periodically varied, said movable valve member being so designed that in its axial mid-position its rotation produces no variation of the crosssections of said ducts, in one of its axial end positions, its rotation produces a maximum periodical variation of said ducts cross-sections in phase with the rotation of said movable valve member and in the opposite axial end position, its rotation produces still a maximum periodical variation of said ducts cross-sections, but with a phase shift, whereby said axial adjustment provides every desired periodical variation of the pressures in said pressure zones of said bearing.

9. The combination of claim 8 which includes a driving connection between said rotatable shaft and said movable valve member.

10. A grinding machine adapted to machine revolution parts, the generatrices of which are slightly cambered, comprising a work piece carrier, a grinding wheel carrier including a spindle mounted in two bearings at least one of which comprises a plurality of circumferentially spaced pressure zones separated by outlet grooves, a grinding wheel carried by said spindle, means to feed separately pressure fluid to each of said zones, a distributor controlling the cross-section ofeatlieast one of said-l feeding duct's a' slidable valve member;ingsaid-rdistributor, the axial position ofwhich controls said cross-section of said .ductaa templet rigid with said work piece carrier ,and ascanning member cooperating owithcsaid ,templet to actuate said slidablevalve member.

'1 1., A grinding machine adapted to machine .lfevolution parts, the generatrices of whichuare sl ghtly Qambere'd, comprising .a work pieceecarrier, a grinding wheel carrier including a spindle mounted in two bearings atleast one of which comprises a plurality of circumferentiallyispaced :pressure zones separated by outlet grooves :and at least two of which are diametrically opposed,

a grinding wheel carried by said spindle, means 4 v including feeding ducts to feed separately pressure fluid to each of said zones, a distributor controlling differentially the cross-sections of the ducts feeding two diametrically opposed pressure zones of said bearing, a slidable valve memher in said distributor, the axial position of which controls said cross-sections of said ducts, a templet rigid with said work piece carrier and a scanning member cooperating with said templet to actuate said slidable valve member.

12. A grinding machine according to claim 11 further comprising a distributor valve to reverse the direction of the axial shift imparted to the grinding wheel spindle so as to obtain at will a concave or a convex part 'with a same templet.

13. A bore grinding spindle comprising a tool carrying shaft mounted in two bearings at least one of which comprises a plurality of circumferentially spaced pressure zones separated by outlet grooves, means to feed separately pressure fluid to each of said zones, and a distributor to control periodically the feeding of at least three of said zones, so as to impart said shaft with a precessional motion around the common axis of said bearings.

14. A jig-borer comprising a tool carrying shaft mounted in two bearings at least one of which comprises a plurality of circumferentially spaced pressure zones separated by outlet grooves, means to feed separately pressure fluid to each of said zones, a distributor to control periodically the feeding of at least three of said zones, so as to impart said shaft with a precessional motion around the common axis of said bearings, and

means rotatively fast with shaft to rotate said I distributor with such a relative speed with respect thereof that each cycle of said shaft precessional motion corresponds to one revolution of the same.

15. In a machine-tool of the type comprising a work-piece carrier, a tool-carrier and means including at least one driving shaft to create a relative motion including a rotation component between said tool and work-piece to machine the latter, the combination with at least two coaxial bearings for said shaft, one at least of said bearings being of the type in which the shaft is fioatably supported by pressure fluid in a stationary bearing surface, the same comprising a plurality of pressure zones separated by outlet grooves, of means to feed separately pressure fluid to each of said zones, a distributor operatively connected with one of said carriers and having a movable member to control the feeding of at least one of said pressure zones and means to actuate said movable member to thereby shift the axis of said shaft with respect to the common axis of said bearings so as to create a fine additional component in said relative motion.

16. In a machine-tool of the type comprising ill) ra 'work'eplece ecarrier,-':a-ctoo1-acarrier and means including at least one .drivingx'shaft :to create a relative motion .includingiairotation component between said tool :and work-piecetomachinezthe latter. the combination with at least iitwo 1coaxial bearings for: saidnshaft, one atileasttofzsaid bearings being of the type in'which theashaft -is floa'tably supported byitpressure fluid in 2a asta.- tionary bearing surface, the .same "comprising a plurality- 'o'f-pressure zones separated by outlet grooves, of means' to feeid separately pressure fluidto each of said zones,iadistributor operatively connected with one of 'said carriers -and having -a movable member to 'control the feeding of 'at"leas'tone of said 1 pressure zones and means'respon'sive to: said relativemotion between "said-tool 1 a'nd work p'iece to actuate said movable member *to thereby shift the axis of said sha'ft with respectyto'the common axis or said two bearings soas to create a fine additional componentin'isa-i-d .rrelative motion as a function thereof.

17. In a machine-tool of the type comprising a work-piece carrier, a tool-carrier and means including at least one driving shaft to create a relative motion including a rotation component between said tool and work-piece to machine the latter, the combination with at least two coaxial bearings for said shaft, one at least of said bearings being of the type in which the shaft is floatably supported by pressure fluid in a sta--v tionary bearing surface, the same comprising a plurality of pressure zones separated by outlet grooves, of means to feed separately pressure fluid to each of said zones, a distributor operatively connected with one of said carriers and having a movable member to control the feeding of at least one of said pressure zones and means including a reference surface, and a scanning member operatively associated with said reference surface and adapted to be responsive to said relative motion between said tool and workpiece to actuate said movable member to thereby shift the axis of said shaft with respect to the common axis of said bearings so as to create a fine additional component in said relative motion as a function of the shape of said reference surface.

18. A grinding-machine adapted to machine non-revolution curved closed surfaces comprising a work-piece-carrier, a grinding-wheel carrier, a spindle mounted on said carrier in two bearings at least one of which comprises a plurality of circumferentially spaced pressure zones separated by outlet grooves and at least two of which zones are diametrically opposed, a grinding-wheel rotatively fast with said spindle, means including feeding ducts to feed separately pressure fluid to each of said zones, a distributor operatively connected with said grinding-wheel carrier, a slidable valve member in said distributor, the axial position of which differentially controls the crosssections of the two feeding ducts leading to said diametrically opposed pressure zones, means on said work-piece carrier to receive a work-piece and to rotate the same, a reference non-revolution curved closed surface rotatively fast with said work-piece rotating means and a scanning member cooperating with said reference surface to actuate said slidable valve member.

19. In a machine-tool of the type comprising a work-piece carrier, a tool-carrier and means including at least one driving shaft to create a relative motion including a rotation component bebearing surface, the same comprising a plurality of pressure zones separated by outlet grooves, of means to feed separately pressure fluid to each of said zones, a distributor operatively connected with one of said carriers and having a rotary member to control cyclically the feeding of at least one of said pressure Zones and means responsive to said rotation component of said relative motion between said tool and work-piece to rotate said rotary member to thereby shift the axis of said shaft with respect to the common axis of said bearings, so as to create a fine additional component in said relative motion as a function of said rotation component.

PAUL GERARD.

HENRI SERANNE.

References Cited in the file of this patent Number Number UNITED STATES PATENTS Name Date Arms May 23, 1944 Arms July 25, 1944 Johnson Oct. 16, 1945 Hoifer Sept. 14, 1948 Martellotti Jan. 25, 1949 Tancred Dec. 13, 1949 FOREIGN PATENTS Country Date Italy Jan. 30, 1926 

